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Publication numberUS5102105 A
Publication typeGrant
Application numberUS 07/614,461
Publication dateApr 7, 1992
Filing dateNov 15, 1990
Priority dateDec 2, 1989
Fee statusPaid
Also published asDE3940004A1, DE3940004C2, EP0436780A1, EP0436780B1
Publication number07614461, 614461, US 5102105 A, US 5102105A, US-A-5102105, US5102105 A, US5102105A
InventorsArno Hamaekers, Werner Hettler, Arnold Simuttis
Original AssigneeFirma Carl Freudenberg
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Hydraulically damped engine mount
US 5102105 A
Abstract
A hydraulically damped engine mount comprises liquid-filled working and equalization chambers 1, 2 which are separated by a resilient partition wall 3 and connected by a damping opening 4. The axially opposing working chamber 1 and the equalization chamber 2 are bounded by essentially non-deformable pistons, the latter being connected to a centrally disposed, annular fitting by means of an liquid-impermeable and elastically deformable annular body. These pistons are rigidly joined to one another by means of a connecting rod 7. The piston 9 bounding the equalization chamber 2 has a piston surface which is at least as large as the piston surface of the partition wall 3. The annular body corresponding to this piston is a first rolling membrane 6 which is curved in the axial direction toward the outside and the partition wall 3 is a second rolling membrane which is curved in the axial direction to extend into the working chamber 1. At its inside, this second rolling membrane is affixed liquid-tight to the connecting rod 7.
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Claims(7)
What is claimed is:
1. In a hydraulically damped engine mount, comprising liquid-filled working and equalization chambers separated by a resilient partition wall and connected by a damping opening, wherein the axially opposing working chamber and the equalization chamber are bounded by essentially non-deformable pistons, the latter being connected to a centrally disposed, annular fitting by means of a liquid-impermeable and elastically deformable annular body, wherein these pistons are rigidly joined to one another by means of a connecting rod penetrating the partition wall parallel to the moving direction in the area of the damping opening and wherein the partition wall is externally affixed to the fitting, the improvement wherein the piston bounding the equalization chamber has a piston surface which is at least as large as the piston surface of the partition wall; wherein an annular body provided between this piston and the fitting is a rolling membrane which is curved in the axial direction toward the outside; wherein the partition wall is a second rolling membrane which is curved in the axial direction to extend into the working chamber; and wherein the second rolling membrane is affixed to the connecting rod in a liquid-tight manner in the area of the damping opening.
2. The engine mount in accordance with claim 1, wherein the piston and the first rolling membrane are configured so as to join one another as one piece.
3. The engine mount in accordance with claim 1, wherein the first rolling membrane is reinforced with an insert of material.
4. The engine mount in accordance with claim 1, wherein the piston is reinforced by means of a reinforcement.
5. The engine mount in accordance with claim 1, wherein the partition wall is bounded by an enlargement in the area of the opening, and wherein the enlargement is elastically widened and pressed against the connecting rod due to an internal prestress.
6. The engine mount in accordance with claim 5, wherein the enlargement contacts the connecting rod in the area of a groove having a matching profile.
7. The engine mount in accordance with claim 5, wherein the enlargement contacts the connecting rod in the area of a cylindrical segment extending parallel to the moving direction and wherein the enlargement can be moved relative to this segment in case of extreme excursions.
Description
BACKGROUND OF THE INVENTION

The invention relates to a hydraulically damped engine mount comprising liquid filled working and equalization chambers which are separated by a resilient partition wall and connected by a damping opening. Opposing one another, the working and equalization chambers are bounded toward the outside by essentially non-deformable pistons. A liquid-impermeable and elastically deformable annular body connects each of these pistons to a centrally disposed, annular fitting. A connecting rod, which penetrates the partition wall parallel to the moving direction in the area of an opening, rigidly connects the pistons. The partition wall is externally affixed to the fitting.

An engine mount of this type is known from the German Patent Publication No. OS 27 27 244. The resulting isolation of engine-induced, acoustically interfering vibrations is less than satisfactory.

SUMMARY OF THE INVENTION

It is therefore an object of the present invention to provide an engine mount of the aforementioned type with improved isolation of acoustically interfering, engine-induced vibrations.

This object, as well as other objects which will become apparent in the discussion that follows, are achieved in accordance with the present invention with an engine mount in which the piston bounding the equalization chamber has a piston surface that is at least as large as the piston surface of the partition wall. Further, the annular body provided in the area of the equalization chamber between the piston and the fitting is a first rolling membrane which is curved in the axial direction toward the outside. The partition wall is a second rolling membrane which is curved in the axial direction to extend into the working chamber; this second rolling membrane is affixed to the connecting rod in a liquid-impermeable connection in the area of the opening.

Due to the configuration of the engine mount in accordance with the invention, loads in are exclusively supported by the resilient properties of one single, elastic annular body bounding the working chamber. Even when tilted during installation, there will be no internal strains directed against one another. Engine-induced, acoustically interfering vibrations of higher frequencies can thus be excellently isolated.

In the event that road-induced vibrations of a great amplitude are introduced, due to its large cross section, the piston bounding the equalization chamber limits the quantity of liquid particles pressed through the damping opening. Vibrations or this kind are thus excellently damped.

The piston bounding the equalization chamber and the first rolling membrane can join one another as one piece and be made of rubber, for example. Manufacture is thus substantially simplified.

It has proved expedient to provide the piston with a reinforcement: for example, a reinforcement plate which is included in the interior by means of vulcanization. In addition to an improved dimensional stability, the dimensionally stable connection to the connecting rod can also be more readily established.

In the area of the opening, the partition wall can be bounded by an enlargement. This enlargement can be elastically widened and, by to an internal prestress, can be pressed against the connecting rod. The use of secondary sealing means to obtain a liquid-tight connection between the partition wall and the connecting rod can thus be omitted in this case.

The connection is particularly tight when the enlargement contacts the connecting rod in the area of a groove having a matching profile. Subsequently, the enlargement and the connecting rod are immovably attached to each other in the axial direction. This is of great advantage in maintaining the engine mount operating characteristics substantially constant over a long period of time.

In another embodiment, the enlargement contacts the connecting rod in the area of a cylindrical segment and can be moved relative thereto in case there are extreme excursions. This prevents undesired damage to the partition wall.

The piston bounding the equalization chamber can be disposed between the fitting stops so that it is only movable between them. Vibrations of an excessive amplitude, and particularly a bursting of the annular body, can thus be effectively prevented.

In order to avoid stopping noises, it has proven to be advantageous when the piston and/or the end stops, on their sides facing each other in moving direction, are provided with elastomeric stopping buffers.

The preferred embodiments of the present invention will now be described with reference to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a longitudinal cross-sectional view of an engine mount according to a first preferred embodiment of the present invention.

FIG. 2 is a top view of the engine mount of FIG. 1.

FIG. 3 is a longitudinal cross-sectional view of an engine mount according to a second preferred embodiment of the present invention.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

The engine mount represented in FIGS. 1 and 2 includes liquid-filled working and equalization chambers 1 and 2, respectively, which are separated by a resilient partition wall 3 and connected by means of a damping opening 4. The working chamber 1 and the equalization chamber 2, which oppose each other in the axial direction, are bounded by essentially non-deformable pistons 16, 9 each of which is connected to a centrally disposed, annular fitting 8 by means of a liquid-impermeable and elastically deformable annular body. The pistons 16, 9 are rigidly connected by means of a connecting rod 7 which penetrates the partition wall parallel to the axial direction in the area of an opening. The partition wall 3 is externally affixed to the fitting 8. The piston 9 bounding the equalizing chamber 2 has a piston surface which is at least as large as the piston surface of the partition wall 3. An annular body 6, which is provided in the area of the equalizing chamber 2 between the piston 9 and the fitting 8, is formed by a first rolling membrane which is curved in the axial direction toward the outside. The partition wall 3 is a second rolling membrane which is curved in the axial direction to extend into the working chamber 1. In the area of its opening, this membrane is affixed, liquid-tight, to the connecting rod 7, as indicated on the enlargement 13 received in a circumferential recess 14 in the rod 7. The piston 16 bounding the working chamber 1 is at the same time configured as a first support and is provided with an internal thread that serves the purpose of attaching the device to be supported, for example an internal combustion engine.

At the same time, the fitting 8 is configured as a second support and, in the bottom area, is provided with an internal thread. The latter serves to attach it to a corresponding base, such as a car body.

A hydrodynamic braking body 17, immersed in the working chamber 1, is additionally provided at the piston 16 bounding the working chamber 1 toward the exterior. This further improves the resulting damping action.

Toward the outside, the working chamber is bounded by a resilient annular body 5 which is able to solely bear the load to be supported. This annular body is provided with opposing, kidney shaped recesses 18 disposed transverse to the moving direction (see FIG. 2). From the top, they engage its profile and, in this direction, impart to it a greater resilience than in a direction extending transverse to this direction. A configuration of this kind is of great advantage when used in an engine mount of a motor vehicle.

The represented engine mount has a good cardanic resilience. High-frequency vibrations are well isolated even when the unit is tilted during assembly and low-frequency vibrations are well damped.

The embodiment of an engine mount of FIG. 3 is distinguished from the embodiment of FIG. 1 and described above in that the first rolling membrane 6 and the second rolling membrane 3 are reinforced by means of highly-flexible material inserts 19. This prevents bursting when extremely elevated pressures occur in the interior of the engine mount. Moreover, the second rolling membrane 3 is provided with an enlargement 13 which contacts the connecting rod in the area of a cylindrical segment and which can be moved relative thereto in case of extreme excursions. The necessary elastic widening of the enlargement during the assembly can be determined by means of simple experiments. It ensures that damage to the engine mount is avoided even in case of extreme excursions of the parts connected by the engine mount. When the engine mount is used in a motor vehicle, such extreme excursions can be caused, for example, when the vehicle drives over a curb.

There has thus been shown and described a novel hydraulically damped engine mount which fulfills all the objects and advantages sought therefor. Many changes, modifications, variations and other uses and applications of the subject invention will, however, become apparent to those skilled in the art after considering this specification and the accompanying drawings which disclose the preferred embodiments thereof. Al such changes, modifications, variations and other uses and applications which do not depart from the spirit and scope of the invention are deemed to be covered by the invention, which is to be limited only by the claims which follow.

Patent Citations
Cited PatentFiling datePublication dateApplicantTitle
US4288063 *May 3, 1979Sep 8, 1981Boge GmbhRubber elastic engine mounts or supports with hydraulic damping, especially for engine suspensions in motor vehicles
US4645188 *Dec 26, 1984Feb 24, 1987Lemforder Metallwaren AgResilient bearing with a hydraulic damper
DE2727244A1 *Jun 16, 1977Jan 5, 1978PeugeotDaempfungsvorrichtung
DE3737252A1 *Nov 3, 1987May 24, 1989Wolf Woco & Co Franz JHydraulisch gedaempftes elastomer-metall-lager
EP0091246A1 *Mar 25, 1983Oct 12, 1983TOYO TIRE & RUBBER CO., LTD .Vibration-absorbing mounting with fluid damping
GB2172083A * Title not available
Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US5284315 *Sep 24, 1992Feb 8, 1994Metzeler Gimetall AgElastic engine mount
US5340093 *Jul 20, 1992Aug 23, 1994Firma Carl FreudenbergHydraulically damped rubber bearing
US5340094 *Apr 9, 1993Aug 23, 1994Boge AgHydraulic damping elastomeric bearing
US5344127 *Dec 10, 1992Sep 6, 1994Firma Carl FreudenbergSwitchable bearing
US5346189 *Nov 24, 1993Sep 13, 1994Firma Carl FreudenbergHydraulically damped rubber bearing
US5408339 *Mar 14, 1994Apr 18, 1995Ricoh Company, Ltd.Image area discriminating device
US5462261 *Sep 9, 1994Oct 31, 1995Firma Carl FreudenbergSwitchable hydraulically damping mount
US5577716 *Nov 22, 1995Nov 26, 1996Firma Carl FreudenbergSingle-thrust bearing for a shock absorber
US5704598 *Sep 9, 1996Jan 6, 1998Bridgestone CorporationVibration isolating apparatus
US6286271 *May 26, 1999Sep 11, 2001Carl Cheung Tung KongLoad-bearing structural member
US6601835 *Mar 29, 2002Aug 5, 2003HutchinsonHydraulic antivibration support
CN101196226BDec 8, 2006May 26, 2010奇瑞汽车股份有限公司Vibration isolation system
DE102007057873B4 *Nov 29, 2007Feb 6, 2014Carl Freudenberg KgLager
Classifications
U.S. Classification267/140.13, 267/219, 180/902
International ClassificationF16M7/00, F16F13/18, F16F13/10
Cooperative ClassificationY10S180/902, F16F13/18
European ClassificationF16F13/18
Legal Events
DateCodeEventDescription
Oct 19, 2010ASAssignment
Effective date: 20101007
Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE ASSIGNEE PREVIOUSLY RECORDED ON REEL 025137 FRAME 0778. ASSIGNOR(S) HEREBY CONFIRMS THE ENTIRE TITLE, RIGHT AND INTEREST, WORLD-WIDE, IN THE PATENTS AND PATENT APPLICATIOSN LISTED ON EXHIBIT 1 ATTACHED HERETO;;ASSIGNOR:FIRMA CARL FREUDENBERG;REEL/FRAME:025150/0938
Owner name: VIBRACOUSTIC GMBH & CO. KG, GERMANY
Oct 15, 2010ASAssignment
Owner name: FIRMA CARL FREUDENBERG, GERMANY
Effective date: 20101007
Owner name: VIBRACOUSTIC GMBH & CO. KG, GERMANY
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:FIRMA CARL FREUDENBERG;REEL/FRAME:025137/0778
Sep 22, 2003FPAYFee payment
Year of fee payment: 12
Sep 24, 1999FPAYFee payment
Year of fee payment: 8
Oct 2, 1995FPAYFee payment
Year of fee payment: 4
Nov 15, 1990ASAssignment
Owner name: FIRMA CARL FREUDENBERG, GERMANY
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNORS:HAMAEKERS, ARNO;HETTLER, WERNER;SIMUTTIS, ARNOLD;REEL/FRAME:005508/0408
Effective date: 19901029